JP2007100821A - Reduction gear with clutch - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a reduction gear with a clutch, wherein squareness is secured between a large gear and an output shaft. <P>SOLUTION: The reduction gear comprises an input shaft 10 connected to the output shaft of a motor, small gears 12, 13 fixed to the input shaft 10, the output shaft 40 connected to a driven device, the large gears 32, 33 rotatably held on the output shaft 40 for rotation in engagement with the small gears 12, 13, and a clutch mechanism 44 provided between the output shaft 40 and the large gears 32, 33. The rotation of the small gears 12, 13 is transmitted to the output shaft 40 via the clutch mechanism 44 and the large gears 32, 33. Sliding bearings 42, 43 are laid between the large gears 32, 33 and the output shaft 44, and thrust rings 20, 21, 22, 23 are fixed to both sides of the small gears 12, 13 fixed to the input shaft 40. Each of the thrust rings 20, 21, 22, 23 has an outer diameter larger than each of the engaging portions 25, 26 between the small gears 12, 13 and the large gears 23, 33. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention reduces the output rotation of the motor by the meshing rotation of the small gear and the large gear and transmits it to the driven device, or increases the output rotation of the motor by the meshing rotation of the large gear and the small gear. The present invention relates to a gear device with a clutch in which a large gear is rotatably installed on an output shaft and a clutch mechanism is provided between the large gear and the output shaft.

  As a conventional device of the gear device with a clutch, a reduction with a clutch shown in FIGS. 3 to 5 will be described as an example. The clutch-equipped speed reducing device shown in FIGS. 3 to 5 is taken as an example, but the clutch-equipped speed increasing device is the same.

  In FIG. 3 which shows an external view of a conventional speed reducer with a clutch, the speed reducer with a clutch provided in the soundproof cover 50 decelerates the input unit 53 connected to the output side of the motor and the rotation transmitted to the input unit 53. And an output portion 54 that transmits to the driven device, and a clutch lever 52 that protrudes outside the soundproof cover 50. When the clutch lever 52 is in the neutral position, an input portion 53 and When the connection with the output unit 54 is interrupted and operated, the input unit 53 and the output unit 54 are connected, and the rotation of the motor is decelerated and transmitted to the driven device. 3 are the high speed large gear 72 and the low speed large gear 73 shown in FIG. 5, and 62 and 63 are the high speed small gear 62 and the low speed small gear shown in FIG. 63. Reference numerals 77a and 77b denote rotation distribution gears shown in FIG.

  As shown in FIG. 4, in the input portion 53, an input shaft 60 to which output rotation of a motor is transmitted is rotatably supported on a main body 55 by bearings 61a and 61b. The input shaft 60 is provided with a high-speed small gear 62 and a low-speed small gear 63, each of which includes a high-speed large gear 72 rotatably held on an output shaft 70 shown in FIG. It meshes with a large gear 73 for low speed. The high-speed small gear 62, the low-speed small gear 63, the high-speed large gear 72, and the low-speed large gear 73 are helical gears. The thrust bearing 65 is provided at the end of the input shaft 60 and receives a thrust force due to the small gears 62 and 63 being constituted by helical gears.

  As shown in FIG. 5, the output shaft 70 connected to the driven device is rotatably held on the main body 55 by bearings 71a and 71b, and the high speed large gear 72 meshed with the high speed small gear 62 and A large gear 73 for low speed meshing with the small gear 63 for low speed is also rotatably supported by bearings 72a, 72b, 73a, 73b. A clutch mechanism 74 that is operated by the clutch lever 52 is provided between the large gear 72 for high speed and the large gear 73 for low speed.

  The clutch mechanism 74 includes an outer peripheral spline that meshes with a spline provided on an inner peripheral surface of a concave portion 72c provided on the high speed gear 72 and a low speed large gear 73 and a concave portion 73c provided on the low speed large gear 73. And a spline provided on the outer periphery of the large-diameter portion 70a of the output shaft 70, and a fitting / removing element 75 having a spline that is always coupled to the spline on the inner periphery. The low-speed large gear 73 or the high-speed large gear 72 and the output shaft 70 are connected to the spline of the outer periphery and the spline of the recess 73c or the recess 72c while being connected to the spline of the large-diameter portion 70a by the operation of the clutch lever 52. And

  That is, the clutch mechanism 74 operates the fitting lever 75 to any one of the positions shown in FIG. 5 with the clutch lever 52, whereby the output shaft 70 and the large diameter gear 72 or the large diameter gear 73 are connected to each other. The rotation of the shaft 60 is decelerated and transmitted to the output shaft 70. That is, when the clutch lever 52 is now operated and the fitting / removal element 75 connects the large gear 73 for low speed and the output shaft 70, the output shaft 70 rotates at a low speed, and the fitting / removing element 75 is rotated by the large gear 72 for high speed and the output shaft. When 70 is connected, the output shaft 70 rotates at a high speed. This operation can be performed so as to adapt to the situation of the driven device. Further, the gear 77a and the gear 77b provided on the output shaft 70 are engaged with the meshing output shaft 78a and the output shaft 78b to drive at a constant speed. In other words, this configuration is applied to a device that needs to drive two driven devices at a constant speed.

  The above-described conventional clutch-equipped speed reduction device has bearings 72a and 72b and bearings 73a and 73b, respectively, in order that the large gear 72 for high speed and the large gear 73 for low speed are rotatably held with respect to the output shaft 70. It is a configuration. In this configuration, since the bearing is provided at a position close to the center of the gear, if a deviation occurs in the position of the bearing, the right angle between the output shaft 70 and the gear cannot be secured, so that the small gear fixed to the input shaft 60 is meshed. This can cause damage to the gear teeth. For this reason, when assembling the speed reducer, it is necessary to perform an operation for strictly ensuring the perpendicularity of the shaft and the gear by adjusting the position of the bearing, and this operation is extremely complicated.

  In view of the above-described problems of the prior art, an object of the present invention is to ensure a perpendicularity between a large gear and an output shaft in a gear device with a clutch.

  An input shaft connected to the output shaft of the motor, a small gear fixed to the input shaft, an output shaft connected to the driven device, and a large gear rotatably held on the output shaft and meshed with the small gear And a clutch mechanism provided between the output shaft and the large gear, wherein the rotation of the small gear is transmitted to the output shaft via the clutch mechanism and the large gear. A diameter of the thrust ring covering the meshing portion of the small gear and the large gear, with a bearing interposed between the large gear and the output shaft, and a thrust ring fixed to both sides of the small gear fixed to the input shaft. It is characterized by having.

  The bearing is a slide bearing, and the slide bearing has a structure in which a large gear is fixed and a minute gap is provided between the slide shaft and the output shaft.

  The slide bearing is composed of two members inserted from both sides of the large gear.

  A gap is formed between the slide bearings constituted by the two members, and this gap is used as an oil chamber for lubricating oil.

  The thrust ring fixed to the input shaft is a shrink fit.

  An input shaft connected to the output shaft of the motor, a small gear fixed to the input shaft, an output shaft connected to the driven device, and a large gear rotatably held on the output shaft and meshed with the small gear And a clutch mechanism provided between the output shaft and the large gear, wherein the rotation of the small gear is transmitted to the output shaft via the clutch mechanism and the large gear. A diameter of the thrust ring covering the meshing portion of the small gear and the large gear, with a bearing interposed between the large gear and the output shaft, and a thrust ring fixed to both sides of the small gear fixed to the input shaft. With this configuration, when the output shaft and the large gear are connected by the clutch mechanism, the axial load on which the large gear acts is received by the slide bearing, and the tip of the large gear is held by the thrust ring. In addition, since the perpendicularity between the output shaft and the large gear is also secured by the thrust ring, the work for securing the perpendicularity between the output shaft and the large gear is simplified when the speed reducer is assembled.

  Since the bearing is a plain bearing, the bearing has a very simple configuration, so that it is easy to process and extremely easy to handle. Further, this slide bearing has a structure in which a large gear is fixed and a minute gap is provided between the slide shaft and the output shaft, so that the peripheral speed of the slide bearing portion during idling is further reduced.

  By configuring the slide bearing with two members that are inserted from both sides of the large gear, it is possible to mount the slide bearing from both sides of the large gear, thereby shortening the time for mounting the slide bearing on the large gear. Furthermore, it has the effect of making the slide bearing small and easy to produce.

  Work to mount the slide bearing without specially processing the hot water chamber for storing the lubricating oil by forming a gap between the sliding bearings composed of the two members and making this gap into the lubricating oil chamber. It has the effect which can be comprised. Further, since the sliding bearing can be mounted from both sides of the gear, the work can be simplified.

  Since the thrust ring fixed to the input shaft is shrink-fitted, the thrust ring and the input shaft can be fixed extremely firmly.

  Hereinafter, an embodiment of the present invention will be described with reference to FIG. Although FIG. 1 is an explanation of a reduction gear with a clutch, it is clear that this reduction gear with a clutch becomes a speed increase device with a clutch if the output shaft and the input shaft are reversed. As a specific example, It describes about the reduction gear with a clutch. In the case of a speed increasing device with a clutch, an output shaft described below serves as an input shaft, and the input shaft serves as an output shaft.

    In FIG. 1, reference numeral 10 denotes an input shaft to which the output rotation of the motor is transmitted. The input shaft 10 is rotatably supported by bearings 17a and 17b on a main body 15 of the speed reducer, and a thrust bearing 18 receives thrust acting on the input shaft 10 when power is transmitted. Further, the input shaft 10 is provided with a high-speed small gear 12 and a low-speed small gear 13, and thrust rings 20 and 21 are fixed on both sides of the high-speed small gear 12. Thrust rings 22 and 23 are fixed on both sides of the small gear 13 for use.

  The input shaft 10 is shown in the assembled state in FIG. 1, but before the assembly, a high-speed small gear 12 and a low-speed small gear 13 are integrally formed on the input shaft 10, and a thrust ring 20, As shown in FIG. 1, after the mounting portions 20 a, 21 a, and 23 a of 21, 22, and 23 are processed, and the thrust rings 20, 21, and 23 are shrink-fitted to the mounting portions 20 a, 21 a, and 23 a of the input shaft 10. Attached to the main body 15.

  The diameters of the thrust rings 20 and 21 are slightly larger than the cutting edge diameter of the small gear 12 for high speed, and the small gear 12 for high speed and the large gear 32 for high speed cover the meshing portion 25. Can be done. Further, the diameters of the thrust rings 22 and 23 are slightly larger than the cutting edge of the low speed small gear 13 as described above, and the low speed small gear 13 and the low speed large gear 33 cover the meshing portion 26. Be able to. The dimension between the thrust ring 20 and 21 is slightly larger than the tooth width of the large gear 32 for high speed. Similarly, the dimension between the thrust rings 22 and 23 is slightly larger than the tooth width of the large gear 33 for low speed.

  With this configuration, when the input shaft 10 is rotated by a motor, the high-speed small gear 12 and the low-speed small gear 13 become a high-speed large gear 32 and a low-speed large gear 33. It meshes and rotates. At this time, the tooth side portions of the large gear 32 for high speed and the large gear 33 for low speed are guided to the thrust rings 20, 21, 22, 23, respectively, so that the small gear 12 for high speed and the large gear 32 for high speed are provided. Further, the teeth of the small gear 13 for low speed and the large gear 33 for low speed can be accurately meshed without contacting each other.

  The output shaft 40 rotatably held by the main body 15 with bearings 19a and 19b is configured to transmit the rotational force to the driven device, and the large gear 32 for high speed and the large gear 33 for low speed are formed by sliding bearings 42, 43 is rotatably provided. The slide bearing 42 is composed of two members. That is, the slide bearing 42 is composed of bearing members 42a and 42b having substantially the same configuration. Similarly, the plain bearing 43 is composed of bearing members 43a and 43b having substantially the same configuration.

  The bearing members 42a and 42b are provided with flanges 42c and 42d, and the width thereof is slightly smaller than the tooth width of the large gear 32 for high speed. The outer diameters of the bearing members 42 a and 42 b can be fixed in the bearing hole 32 a of the large gear 32 for high speed, and the inner diameter thereof is slightly larger than the large diameter portion 40 a of the output shaft 40. Therefore, when the large gear 32 for high speed is rotated by the small gear 12 for high speed, it rotates while sliding between the inner diameter of the bearing member 42a and the large diameter portion 40a.

  Similarly, the plain bearing 43 is composed of bearing members 43a and 43b having substantially the same configuration. The bearing members 43a and 43b are provided with flanges 43c and 43d, and the width thereof is slightly smaller than the tooth width of the large gear 33 for low speed. The outer diameters of the bearing members 43 a and 43 b can be fixed to the bearing hole 33 a of the large gear 33 for low speed, and the inner diameter thereof is slightly larger than the large diameter portion 40 b of the output shaft 40. Therefore, when the large gear 33 for low speed is rotated by the small gear 13 for low speed, it rotates while sliding between the inner diameter of the bearing member 43a and the large diameter portion 40b.

  As described above, the high speed large gear 32 and the low speed large gear 33 rotate while sliding between the large-diameter portion 40a and the large-diameter portion 40b of the output shaft 40, but their tips are thrust rings 20, 21. , 22 and 23, it is possible to prevent meshing per piece. Furthermore, since the plain bearings 42 and 43 are very simple cylindrical shapes, the manufacture thereof is easy, and it is only necessary to select an appropriate material (selection of a material suitable for the load condition of the speed reducer). . Further, since the plain bearings 42 and 43 having such simple shapes need only be processed into a cylindrical shape, high-precision parts can be produced. Therefore, the high-speed large gear 32 and the low-speed large gear 33 are assembled. At this time, the perpendicularity to the output shaft 40 can be obtained reliably without any special operation.

  In FIG. 2, bearing members 42 a and 42 b constituting the sliding bearing 42 are provided with flanges 42 c and 42 d, and the width dimension thereof is slightly smaller than the tooth width of the high-speed large gear 32. Therefore, as shown in FIG. 2, when the bearing members 42a and 42b are mounted on the high-speed large gear 32, a groove 34a is formed over the entire circumference of the large-diameter portion 40a at the center. Similarly, the bearing members 43a and 43b constituting the slide bearing 43 are provided with flanges 43c and 43d, and the dimension in the width direction is slightly smaller than the tooth width of the large gear 33 for high speed. Therefore, as shown in FIG. 2, when the bearing members 43a and 43b are mounted on the high-speed large gear 33, a groove 34b is formed over the entire circumference of the large-diameter portion 40b at the center.

  The above-described sliding bearings 42 and 43 are not particularly limited to sliding bearings in the present invention, and the sliding bearings 42 and 43 are substantially the same even if radial bearings or radial roller bearings, which are ordinary bearings, are used. The effect of can be obtained. That is, even when a normal bearing is used between the large gear 32 for high speed and the large gear 33 for low speed and the output shaft 40, the thrust rings 20 and 21 are connected to the large gear 32 for high speed and the small gear for high speed. Since the portion of the meshing portion 25 of the gear 12 is guided, the squareness of the large gear 32 for high speed and the output shaft 40 is maintained, and the meshing portion 25 portion is prevented from meshing with each other. Similarly, the thrust ring 22, 23 guides the portion of the meshing portion 26 of the low speed large gear 33 and the low speed large gear 33 and the high speed small gear 12, so that the low speed large gear 33 and the output shaft 40. This prevents the meshing per piece at the meshing portion 26 from being maintained.

  In the above description of the speed reducer with clutch, the large gear 32 for high speed and the large gear 33 for low speed are provided on the output shaft 40 via bearings. However, in the case of the speed increasing device with clutch, the output shaft 40 is provided. Is an input shaft connected to the motor, and the input shaft 10 is an output shaft. However, the relationship between the large gear 32 for high speed and the large gear 33 for low speed and the output shaft 40 is the same as the speed reducer with clutch and the speed increase device with clutch. Therefore, when this embodiment is understood as a speed increasing device with a clutch, the output shaft 40 is referred to as the input shaft 10 and the input shaft 10 is referred to as the output shaft 40.

  The grooves 34a and 34b are connected to a passage 35 provided in the output shaft 40 via passages 36a and 36b. The passage 35 is configured to be supplied with lubricating oil from a swivel joint 37 provided at the open end of the output shaft 40. Accordingly, the lubricating oil supplied through the passage 35 and the passages 36a and 36b is Lubricating oil is supplied to the grooves 34a and 34b and supplied between the large diameter portion 40a and the bearing members 42a and 42b and between the large diameter portion 40b and the bearing members 43a and 43b. Since the grooves 34a and 34b are formed over the entire circumference of the large diameter portion 40a and the large diameter portion 40b, the large gear 32 for high speed, the large gear 33 for low speed, the bearing members 42a and 42b, and the bearing member. Lubricating oil is always supplied between 43a and 43b.

  Details of the clutch mechanism 45 and the slide bearings 42, 43 provided between the high speed gear 32 and the low speed gear 33 will be described with reference to FIG. 2 which is a partially enlarged view of FIG.

  The clutch mechanism 44 is provided in a portion where the large gear 32 for high speed and the large gear 33 for low speed are opposed to each other. The spline 48 provided in the large diameter portion 40c, the large gear 32 for high speed, and the low speed large gear 33 are provided. Splines 49 a and 49 b provided in the recesses 39 a and 39 b of the large gear 33 and the fitting / removing element 45 are configured. The spline 46a provided on the inner periphery of the fitting / removing element 45 is always meshed with the spline 48 provided on the large diameter portion 40c and can move in the lateral direction. The splines 49a and 49b provided on the outer periphery of the fitting / removing element 45 are configured to mesh with any one of the splines 49a and 49b of the recesses 39a and 39b when the fitting / removing element 45 is moved in either the left or right direction. The movement of the fitting / removing element 45 is performed by a fork member connected to a recess 47 provided in the fitting / removing element 45 by operating the clutch lever 52, although not shown.

  When the fitting / removing element 45 of the clutch mechanism 44 is in the position shown in FIG. 2, the output shaft 40 is in the “disengaged” position where the high-speed large gear 32 and the low-speed large gear 33 are not connected. The rotation of the large gear 32 and the low speed large gear 33 transmitted from the input shaft 10 is transmitted from the high speed small gear 12 and the low speed small gear 13 and idles. When the fitting / removing element 45 is operated to the right (position where the large gear 32 for high speed and the input shaft 60 are connected), the fitting / removing element 45 moves while being connected to the spline 48, and the splines 46a and 49a are connected. Therefore, the large gear 32 for high speed and the output shaft 40 are connected. Similarly, when the fitting / removing element 45 is moved to the left to connect the large gear 33 for low speed and the input shaft 60), the fitting / removing element 45 moves while being connected to the spline 48, and the splines 46b and 49b are connected. Therefore, the low speed large gear 33 and the output shaft 40 are connected. The clutch mechanism 44 has the same configuration as the clutch mechanism 74 shown in FIG.

  In the present embodiment described above, the configuration other than the configuration shown in FIGS. 1 and 2 (excluding the clutch mechanism) is the same as the configuration of the prior art, so the description thereof is omitted.

  The operation of this embodiment will be described below. First, when the clutch lever 52 is not operated and the fitting / removing element 45 of the clutch mechanism 44 meshes only with the output shaft 40, the small gear for high speed is generated by the rotation of the motor transmitted to the input shaft 10. 12 and the small gear 13 for low speed rotate. This rotation is transmitted to the large gear 32 for high speed and the large gear 33 for low speed that mesh with the small gear 12 for high speed and the small gear 13 for low speed. At this time, the large gear 32 for high speed and the large gear 33 for low speed are supported by the slide bearings 42 and 43, and the output shaft 40 remains stopped only by rotating. At this time, the output shaft 40, the high-speed large gear 32, and the low-speed large gear 33 are only idling, so that the slide bearings 42 and 43 have only a slip that does not act on the load.

  Next, when the rotation of the motor is stopped and the clutch lever 52 is operated to move the fitting / removing element 45 of the clutch mechanism 44 to the right in FIG. 2, the fitting / removing element 45 is connected to the spline 48 of the large-diameter portion 40c. As it is, the spline 46b meshes with the spline 49a of the large gear 32 for high speed. When the motor is driven in this state and the input shaft 10 is rotated, the rotation is transmitted from the high speed small gear 12 to the output shaft 40 by the fitting / removing element 45 via the high speed large gear 32. At this time, the low-speed large gear 33 that meshes with the low-speed small gear 13 also rotates. However, since the connection with the output shaft 40 is cut off by the fitting / removing element 45 of the clutch mechanism 44, it is idling. .

  When the rotation is transmitted to the output shaft 40 in this manner, the two output shafts 78a and 78b are driven at a constant speed by the gears 77a and 77b shown in FIG. 5 and transmitted to the driven device. In this way, when the rotation of the motor is transmitted to the driven device, a load in the direction perpendicular to the axis acts between the small gear 12 for high speed and the large gear 32 for high speed according to the load. However, since the large gear 32 for high speed rotates together with the output shaft 40, a load in the direction perpendicular to the axis acts on the slide bearing 42. There is a minute gap between the inner surfaces of the bearing members 42a and 42b of the slide bearing 42 and the outer periphery of the large-diameter portion 40a. The large gear 32 for high speed tends to fall slightly. 20 and 21 are supported. For this reason, it is possible to reliably prevent one-piece contact due to meshing rotation between the high-speed small gear 12 and the high-speed large gear 32.

  As described above, in the present embodiment, the case where the fitting / removing element 45 is operated in the right direction has been described. However, when the fitting / removing element 45 is operated in the left direction, the output shaft 40 and the large gear 33 for low speed are provided. The large gear 32 for high speed and the output shaft 40 are not connected. Accordingly, the rotation of the motor transmitted to the input shaft 10 is distributed at a constant speed from the output shaft 40 through the large gear 33 for low speed from the small gear 13 for low speed to the driven device by the gears 77a and 77b. Is done.

  When the rotation of the motor transmitted to the input shaft 10 is transmitted from the high speed small gear 12 via the high speed large gear 32, the speed is reduced at a high speed, and the low speed small gear 13 is used for the low speed. Is transmitted through the large gear 33, the speed is reduced at a low speed. Which of these should be selected can be selected according to the working conditions required by the driven device.

Sectional drawing of the Example of this invention. The elements on larger scale of FIG. Outline drawing of conventional reduction gear with clutch AA sectional view of FIG. BB sectional view of FIG.

Explanation of symbols

10 Input shaft (output shaft)
12 small gear for high speed 13 small gear for low speed 15 main body 20, 21, 22, 23 thrust ring 25, 26 meshing portion 32 large gear for high speed 33 large gear for low speed 40 output shaft (input shaft)
42, 43 Slide bearing (bearing)
44 Clutch mechanism 45

Claims (5)

An input shaft connected to the output shaft of the motor, a small gear fixed to the input shaft, an output shaft connected to the driven device, and a large gear rotatably held on the output shaft and meshed with the small gear And a clutch mechanism provided between the output shaft and the large gear, wherein the rotation of the small gear is transmitted to the output shaft via the clutch mechanism and the large gear. ,
A bearing is interposed between the large gear and the output shaft, and a thrust ring is fixed on both sides of the small gear fixed to the input shaft. The thrust ring has a diameter larger than the meshing portion of the small gear and the large gear. A gear device with a clutch having an outer diameter.   2. The gear device with a clutch according to claim 1, wherein the bearing is a slide bearing, and a large gear is fixed to the slide bearing and a minute gap is provided between the slide shaft and the output shaft.   The gear device with a clutch according to claim 2, wherein the slide bearing is constituted by two members inserted from both sides of the large gear.   4. A gear device with a clutch according to claim 3, wherein a gap is formed between slide bearings constituted by the two members, and the gap is used as an oil chamber for lubricating oil. The gear device with a clutch according to any one of claims 1 to 4, wherein the thrust ring fixed to the input shaft is shrink-fitted.

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